Classifications

• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
  • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
  • F16F15/22—Compensation of inertia forces
  • F16F15/26—Compensation of inertia forces of crankshaft systems using solid masses, other than the ordinary pistons, moving with the system, i.e. masses connected through a kinematic mechanism or gear system
  • F16F15/264—Rotating balancer shafts
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
  • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
  • F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
  • F16F15/14—Suppression of vibrations in rotating systems by making use of members moving with the system using masses freely rotating with the system, i.e. uninvolved in transmitting driveline torque, e.g. rotative dynamic dampers
  • F16F15/1407—Suppression of vibrations in rotating systems by making use of members moving with the system using masses freely rotating with the system, i.e. uninvolved in transmitting driveline torque, e.g. rotative dynamic dampers the rotation being limited with respect to the driving means
  • F16F15/1414—Masses driven by elastic elements
  • F16F15/1421—Metallic springs, e.g. coil or spiral springs

Definitions

• the invention relates to a mass balance module with a housing which is attached to a crankcase, wherein the mass balance module with crankcase a crankshaft having a balance shaft with variable imbalance masses.
• a balancing shaft is usually provided whose direction of rotation must be opposite to the direction of rotation of the crankshaft.
• the balance shafts are connected, for example via a chain, with a gear arranged directly on the crankshaft.
• a gear wheel which is secured against rotation with the crankshaft, directly to a toothed wheel which is arranged so as to be non-rotating on one of the balance shafts.
• Mass balance modules often integrate other components and ancillaries in the prior art.
• the balancing shafts which can be found in the prior art are driven by the crankshaft either with endless traction means or gears and can not be decoupled from the crankshaft.
• the balance shafts are driven at each time of operation of the reciprocating engine, since they are directly connected to the crankshaft via the above-mentioned traction means or gears.
• Mass balance shafts are formed from a centric shaft and attached or structurally integrated imbalance masses. The use of static imbalance masses does not make it possible to improve the operation of the mass balance system.
• the unbalance arrangement is kept adjustable with respect to the axis of the balancing shaft as a function of the speed, so that the phase position and the size of the centrifugal forces generated as compensating forces are defined variable.
• the imbalance arrangement can be adjusted automatically, namely by the action of centrifugal force against a return spring, or with the aid of a controllable adjusting device.
• the proposed in the prior art arrangement for unbalanced masses shows a speed-dependent rotation of the mass against the shaft.
• the proposed arrangement unbalance masses are adjusted within the space prescribed by the balance shaft space. The method thus allows only a slight adjustment of the imbalance and thus a small influence on the moments of the reciprocating engine.
• the object of the invention is to produce a balancing shaft system which is adaptable in a simple manner to the parameters and conditions of a reciprocating engine.
• balance shaft with adjustable imbalance masses but with a simple and space-saving construction. hen. to provided. This makes it possible to fine tune the system to the conditions of the reciprocating engine.
• the mass balance module according to the invention is detailed in the figures and in the description below.
• FIG. 1 shows a longitudinal section through a mass balance module.
• FIGS. 2 and 3 show an imbalance mass according to the invention
• FIGS. 4 and 5 show a further alternative embodiment of the imbalance mass
• FIG. 1 shows a longitudinal section through a mass balance module of the prior art.
• the mass balance module has a housing 13 which is attached to an opening of the crankcase 15, in which a crankshaft is mounted.
• the crankcase 15 is placed on a crank bed 2, which is closed at the bottom by an oil pan 3.
• One or more balance shafts 7 are rotatably mounted in the housing 13.
• the balance shafts 7 may be mounted in the housing 13 by means of plain bearings or rolling bearings. Furthermore, it is possible to store the balance shafts 7 directly in the housing 13 without any plain bearing bushings or roller bearings.
• the counterweights 10, 1 1 can be equipped with rotationally symmetrical, the contour of the counterweights following protective caps.
• the protective caps are located on the opposite side of the counterweights.
• the housing 13 is attached to an opening 15 of the crankcase of the internal combustion engine.
• the balancing shaft 7 is connected to the crankshaft of the internal combustion engine via torque-transmitting elements such as, for example, a chain, gears, belt drives.
• crankcase 15 and mass balance module 13 The structure of the entire system of crankcase 15 and mass balance module 13 is carried out according to the requirements of the internal combustion engine with one or more balance shafts, possibly with a Lancester compensation system.
• FIG. 2 shows an embodiment according to the invention of an imbalance mass along a longitudinal section through a balancing shaft.
• the balance shaft 7 serves as a carrier of a static imbalance mass 4, which is shown as an example.
• the imbalance mass sits along a contact surface 9 on the balance shaft 7. It can be applied, for example, on the balance shaft 7 in a shrink fit.
• the static imbalance mass 4 contains an inner housing 5.
• a material of high density is introduced and serves as an inner imbalance mass 6.
• the inner housing can have a cylindrical shape.
• the inner imbalance mass 6 fills the area of the inner housing, which is close to the shaft 7 almost completely.
• the inner unbalanced mass 6 tapers to an unbalanced hub 17. It forms an axis for a disc spring package 8, which surrounds the tapered portion of the inner imbalance mass.
• the disc spring package 8 fills the space to the outward boundary of the inner housing 5.
• the disc springs are preferably circular and have a central opening.
• the design of the imbalance mass and the disc springs is not limited to the shape shown. Rather, all forms and spatial variants that lead to the solution according to the invention can be used.
• the imbalance hub 17 does not reach to the outer boundary of the inner housing, but leaves a damping chamber 10 free, which is filled with damping media, for example with hydraulic oil.
• the compensation system consists of the constant imbalance mass 4, in which the package of housing 5, disc springs 8 and inner imbalance mass 6 is installed with high density as an assembly. This package is pressed together into the static imbalance mass 4 so as to allow oil tightness. The hydraulic oil for damping the internal imbalance 6 is pressed together with the package.
• the most varied spring characteristics of the overall system can be realized.
• the disc spring assemblies are assembled with different pairs of disc springs to influence the spring characteristic and the spring characteristic.
• progressive or linear spring characteristics can be achieved. Advantages result from the simple design with fewer components and the elimination of a scheme.
• An advantage is the damping of the system by filling with oil, so as to narrow speed changes and rotational irregularities of the drive motor and the resulting possibly resulting swing of the spring-mass system.
• the internal imbalance mass o must have a high density, as for example with composites of heavy metals with high
• FIG. 4 shows an embodiment with an active control of an imbalance mass.
• the designation of the static imbalance mass 4 and the inner imbalance mass 6 corresponds to the embodiment according to FIG. 2.
• the damping medium in this case an oil, is not only used for the purpose of damping but used to control the position of the inner imbalance mass 6.
• an oil supply channel 1 1 is created in the balance shaft 7.
• the oil supply channel 1 1 is located in the center of the balance shaft 7.
• Perpendicular to the oil supply channel 1 1 extends another channel 1 1 ', which ends at an oil passage 14 of the static imbalance mass.
• the oil channel 14 of the static imbalance mass has a connection 12 to the damping chamber 10 of the inner housing 5.
• the inner imbalance mass 6 is pressed against the disk spring packs 8 or pushed away from them to the bottom of the inner housing 5 , As a result, the radical position of the inner imbalance mass 6 can be steplessly positioned under prestress.
• Ball-shaped seals 16 close the oil channels. These static imbalance mass 4 is also attached by means of shrink fit on the balance shaft 7. In order to prevent deflection of the balance shaft 7 due to the shrink fit, an assembly of the components by means of dowel pins is alternatively possible. With dowel pins while the bore openings of the oil passages can be closed at the same time and the ball-shaped seals can be omitted.
• a map-controlled mass balancing module can be produced, which determines the degree of mass balancing via specific engine characteristic values, such as, for example, Speed, load, engine temperature, etc. controls.
• the radial position of the total imbalance can be adjusted independently of the speed of the balance shaft and the crankshaft.

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• Engineering & Computer Science (AREA)
• General Engineering & Computer Science (AREA)
• Physics & Mathematics (AREA)
• Acoustics & Sound (AREA)
• Aviation & Aerospace Engineering (AREA)
• Mechanical Engineering (AREA)
• Shafts, Cranks, Connecting Bars, And Related Bearings (AREA)

Applications Claiming Priority (2)

Publications (1)

Family

ID=48628664

Family Applications (1)

Country Status (2)

Citations (5)

Family Cites Families (3)

• 2012
  • 2012-06-27 DE DE102012211049.6A patent/DE102012211049A1/de not_active Withdrawn
• 2013
  • 2013-06-14 WO PCT/EP2013/062403 patent/WO2014001104A1/fr not_active Ceased

Patent Citations (5)

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